Heat-exchange dryer apparatus, system and method

ABSTRACT

Various embodiments of a heat-exchange dryer apparatus are disclosed. In one embodiment, a heat-exchange dryer apparatus includes a desiccant cartridge comprising desiccant material, a purge-air reservoir secured to the desiccant cartridge, and a compressed-air conduit disposed inside the purge-air reservoir. In another embodiment, a vehicle air-brake system includes an air compressor, a desiccant cartridge comprising desiccant material, and a heat exchange dryer apparatus disposed between the compressor and the desiccant. The temperature of the compressed air is decreased while the temperature of the purge air is increased and the desiccant adsorbs a greater amount of contaminants form the compressed air for improved drying.

BACKGROUND

The present invention relates to an air-brake dryer apparatus and dryersystem for use in commercial vehicles.

Commercial vehicles such as trucks and buses and other large commercialvehicles are typically equipped with a compressed air system in whichthe brakes of the vehicle are actuated by compressed air. Typically, anair compressor is operated by the vehicle engine and generatespressurized air for the operation of air brakes and other devices thatrely on pneumatic air. The operation of an air compressor inherentlyraises the temperature of the air and also produces contaminants such asoil. The accumulation of water, oil and other contaminants presentproblems that can adversely affect the operation of the brake system andother devices that rely on the compressed air. During cold weather, forexample, the moisture entrained in the air brake system may freeze andcause the components of the air brake system to freeze, thus renderingthe system inoperable. At the other extreme during hot weatherconditions, the compressed air can accommodate a higher concentration ofmoisture flowing through the system.

Vehicle air systems generally include a filter and a desiccant air-dryerto remove contaminants that accumulate, for example, coalesced oil, oilvapor and water vapor of the compressed air. The desiccant can also beregenerated, however, during the hot weather conditions, a greateraccumulation of moisture and other contaminants can cause the desiccantto become saturated. In addition, a higher concentration of oil can coatthe desiccant and the dryer will cease to perform the functions ofproviding dry air.

SUMMARY

Various embodiments of a heat-exchange dryer apparatus are disclosed. Inone embodiment, a heat-exchange dryer apparatus for a vehicle air-brakesystem includes a desiccant cartridge comprising desiccant material, ahousing of a purge-air reservoir secured to the desiccant cartridge, anda compressed-air conduit disposed inside the housing of the purge-airreservoir.

In another embodiment, a heat-exchange dryer apparatus comprises adesiccant cartridge containing desiccant material, a compressed-airconduit in fluid communication with the desiccant material, and ahousing of a purge-air reservoir is disposed remote from the desiccantcartridge and nested in the compressed-air conduit.

In another embodiment, an air-brake dryer system for commercial vehicleincludes an air compressor and a heat-exchange dryer apparatus. Theheat-exchange dryer apparatus includes a desiccant cartridge comprisingdesiccant material, and a first vessel and a second vessel disposedbetween the compressor and the desiccant material and the vessels arearranged such that the second vessel is nested in the first vessel.

Various methods for drying air in a vehicle air-brake system are alsodisclosed. In one embodiment a method includes passing compressed airthat has exited a compressor against a first surface of a wall that isin contact with purge air on the opposite surface, and followed bypassing the compressed air through a desiccant material. The temperatureof the compressed air is decreased while the temperature of the purgeair is increased. The desiccant adsorbs a greater amount of contaminantsform the compressed air for improved drying.

BRIEF DESCRIPTION OF THE DRAWINGS

The various embodiments of the present invention can be understood withreference to the following drawings. The components in the drawings arenot necessarily to scale. Also, in the drawings, like reference numeralsdesignate corresponding parts throughout the several views.

FIG. 1 is a schematic illustration of components of the air-brake systemin a commercial vehicle, according to an embodiment of the invention;

FIG. 2 is a perspective view of a heat-exchange dryer apparatus showingthe internal components, according to an embodiment of the presentinvention;

FIG. 3 is a perspective view of an alternative heat exchange dryerapparatus showing the internal components, according to an embodiment ofthe present invention;

FIG. 4 is a schematic representation of a commercial vehicle air brakesystem, according to another embodiment of the invention.

FIG. 5 is a schematic illustration of a portion of heat-exchange dryerapparatus, according to an embodiment of the present invention; and

FIG. 6 is a schematic illustration of a portion of heat-exchange dryerapparatus showing the internal components, according to an alternativeembodiment of the present invention.

DETAILED DESCRIPTION

FIG. 1 illustrates a schematic representation of a vehicle air-brakesystem 10 in accordance with an embodiment of the present invention.Although the detailed description of this invention describes theinvention in specific relation to a compressed air system used in aheavy truck brake system, one skilled in the art should appreciate thatthe scope of this invention includes compressed air systems used inother vehicles, including other commercial vehicles, to operate brakesas well as other pneumatically-operated devices.

An air compressor 12 is the source of compressed air and can be drivenby a vehicle engine (not shown) in a conventional manner The cycling onand off of the compressor 12 is controlled by a governor 14 whichtransmits signals to compressor 12 via control line 16. Pressurized airexits the compressor 12 and passes through a heat-exchange dryerapparatus 20 which includes a desiccant cartridge 22 that containsdesiccant material (not shown) and a purge-air reservoir 23 contained bya vessel or housing 24. Moisture, oil and other contaminants are usuallyremoved from the pressurized air before it is stored in supply tank 30for use in the air brakes and other downstream uses. The vehicleair-brake system 10 may include additional storage tanks such as primaryreservoir 32 and secondary reservoir 34 so that the volume of treatedair reserved for the braking system is within specified safetyguidelines. Check valves 36 and 38 prevent backflow of treated air outof the storage tanks 32 and 34, respectively.

To ensure adequate supply of compressed air for the brakes, the vehicleair-brake system typically operates at two different modes known as thecharging mode and the purging mode. The air-brake system operates withina pressure that generally ranges from about 130 psi to about 180 psi.During operation of the vehicle a portion of the compressed air supplyis depleted when the brakes are applied by the driver. As a result thepressure of the system drops downstream from the compressor. Additionaltreated air is needed for the system. The governor 14 signals thispressure drop to the compressor 12 via control line 16 and initiates thecharging mode. During the charging mode the compressor 12 generatesadditional compressed air and feeds the compressed air through thecompressor discharge line 18 and to the inlet port 19 of theheat-exchange dryer apparatus 20. The compressed air flows into thevessel or housing 24 of the purge-air reservoir 23 portion of theheat-exchange dryer apparatus 20 and is treated by the desiccantcontained in desiccant cartridge 22, as will be further explained indetail below. The treated air flows out of the heat-exchange dryerapparatus 20 via supply port 25 and through supply line 26 to the supplytank 30 and also to supply tanks 32 and 34 via air lines 31 and 33,respectively. Treated air also flows into the vessel or housing 24 ofthe purge-air reservoir 23.

The vehicle air-brake system 10 remains in the charge cycle until thepressure builds to a predetermined cutout pressure set on the governor14. At the cutout pressure, the compressor 12 unloads and aircompression is stopped. Once the compressor is stopped the purge cyclebegins in order to regenerate the desiccant for the next charge cycle.The governor 14 signals a purge valve 71 (FIG. 2) disposed in the vesselor housing 24 of the purge-air reservoir 23 to open which causes thepressure inside the purge-air reservoir to drop. As a result of thepressure differential the treated purge air is forced back through thedesiccant and pulls the water and other contaminants back out of thedesiccant. Check valves throughout the system, for example check valves36 and 38 prevent the treated supply air from being bled back into thepurge-air reservoir 23 as it is gradually depressurized. The reductionof the pressure also exhausts the compressed air surrounding thedesiccant in the desiccant cartridge 22, which rapidly carries out themoisture, oil droplets and other contaminates entrained on the desiccantmaterial through purge valve in the purge-air reservoir 23 and out tothe environment. The purge-air reservoir 23 can remain open to theenvironment and the pressure within the heat-exchange dryer apparatus 20can remain reduced until the governor 14 signals the compressor 12 tocharge. When the pressure in the supply reservoirs 30, 32 and 34 dropbelow a predetermined level caused by use of the vehicle's air brakes,the charge cycle begins again and the compressor 12 begins to compressair and purge valve disposed in the vessel or housing 24 of thepurge-air reservoir closes thereby permitting heat-exchange dryerapparatus 20 to clean and dry the compressed air entering fromcompressor discharge line 18 and into the inlet port 19. FIG. 2 is aperspective view of heat-exchange dryer apparatus 20 of vehicleair-brake system 10 (FIG. 1). In one embodiment, heat-exchange dryerapparatus 20 includes a desiccant cartridge 22 comprising desiccantmaterial 40, and a vessel or housing 24 containing purge-air reservoir23 that is secured to the desiccant cartridge. Desiccant material 40 iscontained within desiccant enclosure 41 such that an annular space 42exists between desiccant enclosure 41 and cartridge 22. Heat-exchangedryer apparatus 20 also includes a compressed-air conduit 44 disposedinside the vessel or housing 24 of the purge-air reservoir. Thecompressed-air conduit is positioned within the air-brake system betweenthe compressor 12 and the desiccant material 40. As shown in oneembodiment of FIG. 2, the compressed-air conduit 44 is disposed insidethe vessel or housing 24 of the purge-air reservoir such that thecompressed-air conduit is surrounded by purge air contained in thepurge-air reservoir 23. In one example arrangement the compressed-airconduit 44 is in fluid communication with an inlet port 19 (FIG. 1) ofthe purge-air reservoir housing 24 and the desiccant material 40.

Compressed-air conduit 44 has a proximal end 45 and a distal end 46,both of which can be connected or secured in different arrangements. Forexample, the proximal end 45 of compressed-air conduit 44 can beconnected directly to the inlet port 19 of the purge-air reservoirhousing 24 and the distal end 46 connected to an outlet port 49 of thepurge-air reservoir housing 24. In another arrangement, a purge-valveassembly 71 is disposed between the inlet port 19 and the compressed-airconduit 44, and therefore, the proximal end 45 of compressed-air conduitis connected to purge-valve assembly 71 and the distal end 46 isconnected to the outlet port 49 of purge-air reservoir housing 24.Outlet port 49 is proximate annular space 41 and the compressed air thatflows inside the compressed-air conduit is directed into the secureddesiccant cartridge 20 along annular space 42. The compressed air iscooled by the purge air that resides inside the vessel or housing 24 ofthe purge-air reservoir and is further cooled via “skin cooling” by heattransfer along the desiccant cartridge 22 that is exposed to theatmosphere. Compressed-air conduit 44 can include crimped sections thatforms shoulder 75 near the proximal end 45 and shoulder 76 near thedistal end 46. The shoulders accommodate seals 47 and 48, respectively,to pressure-seal the compressed-air conduit 44 within the purge-airreservoir housing 24.

Heat-exchange dryer apparatus 20 also includes a treated-air conduit 50positioned within the purge-air reservoir 24 such that it is in fluidcommunication with the desiccant material 40 and supply port 52, and anoptional second supply port 54. Treated air from the desiccant material40 flows through treated-air conduit 50 and through at least one supplyport 52, 54 to the supply tank 30 (FIG. 1). Treated-air conduit 50 has aproximal end that is connected to an inlet port 53 of the housing 24 ofthe purge-air reservoir and a distal end that is secured to an outletport of the housing 24. Treated-air conduit 50 also has crimped sectionsthat form shoulders 77 and 78 for placement of internal seals 57 and 58,for example o-ring seals. Treated-air conduit 50 includes an opening 70that allows the treated air to flow between the treated-air conduit 50and the purge-air reservoir inside the housing 24. For example, aportion of the treated air flowing through treated-air conduit 50 ispurge-air retained in the purge-air reservoir 24 when the air is flowingfrom the desiccant cartridge to the outlet port, for example supplyports 52, 54, of the housing 24. The opening 70 can also be located inpurge-air reservoir housing 24 along channel 73 where treated air exitsthe desiccant and enters the treated-air conduit.

Compressed-air conduit 44 is shown as a vertical pipe and the shape oftreated-air conduit 50 is shown as having a slight “S” curve and isoriented at an angle, α, of at least zero degrees relative to thehorizontal axis, as denoted by axis X. The angle alpha can range fromzero degrees to 180 degrees. Compressed-air conduit 44 and treated-airconduit 50 may straight, curved or sloped to include bends and curves ofvarious slopes, provided the slope of any section is greater or equal tozero. The compressed-air conduit 44 and treated-air conduit 50 shouldnot have any changes in the direction of the slope, for example, both apositive and negative slope, so as to create valleys where condensedfluid or contaminants may collect or pool. Condensed fluids that collectin compressed-air conduit 44 and treated-air conduit 50 could freeze incold weather and create blockages in the air-brake system.

The profile shapes and dimensions of compressed-air conduit 44 andtreated-air conduit 50 can vary. For example, the conduits have acircular cross-section, however, several alternative cross-sections, forexample, rectangular, oval, polygonal, etc., may be used. The diameteror cross-section dimensions can also vary. For example, the dimensionsof the conduit can have an outer diameter that ranges from 0.25 to 1inch, or in another embodiment a nominal outer diameter that isapproximately 0.625 inch and a wall thickness of 0.035 inches.

The heat-exchange dryer apparatus 20 described above facilitates a heattransfer between the untreated air in the compressed-air conduit and thetreated air that resides in the housing 24 of the purge-air reservoir23. In one embodiment, the compressed-air conduit 44 is made of amaterial that has a high heat transfer coefficient, for example, a heattransfer coefficient that is at least about 100 W/mK., in anotherembodiment, from about 100 W/mK to about 300 W/mK, and in anotherembodiment from about 120 W/mK to about 300 W/mK. The conduit 44 can bemade of high thermal conductivity materials, including but not limitedto, aluminum, copper, gold, silver, brass and alloys or mixturesthereof. During the charging cycle described above, the compressed airgenerated by the compressor is passed against the inside surface ofcompressed-air conduit 44 which is in contact with the purge air on theopposite wall surface, the outside surface of compressed-air conduit 44.The heat conducts through the wall of the compressed-air conduit 44 toincrease the temperature of the purge air and to decrease thetemperature of the incoming compressor air. Accordingly, materialshaving a greater heat transfer coefficient will affect a greater heattransfer between these untreated and treated air fluids.

Upon completion of the charge mode described above with respect to FIG.1, the purge mode eliminates the accumulated water and contaminants fromthe system and reactivates the desiccant material. The liquid andcontaminants that are ejected out of the purge valve assembly 71 whenthe governor 14 provides a signal for the purge mode. Purge valveassembly can include a hose adaptor 72 if it is desirable to attach ahose or fitting to convey the purge residue. The drop in pressure in thepurge-air reservoir 23 causes the purge air to flow in the reversedirection and through the opening 70 of treated-air conduit 50. Thepurge air flows through the desiccant cartridge and through thecompressed-air conduit 44 to regenerate the desiccant material 40. Thepurge air which was heated via contact with the compressed-air conduit44 during the charge cycle is warmer for better regeneration of thedesiccant.

In summary, during operation of the vehicle air-brake system 10 (FIG. 1)in the charge mode, hot compressed air generated by the compressor 12enters the heat-exchange dryer apparatus 20 through inlet port 19 ofpurge-air reservoir housing 24. The hot air travels through thecompressed-air conduit 44 and heat is transferred through the conduit tothe relatively cooler purge air that resides in the purge-air reservoirhousing 24. The compressed air moving to the desiccant becomes coolerand moisture condenses within the compressed-air conduit 44 and agreater amount of contaminants are adsorbed by the desiccant due to thelower temperature of the air that passes through it. The treated purgeair that accumulates in the purge-air reservoir during the charge cycleregenerates the desiccant during the purge cycle as described above. Thepurge air becomes gradually warmer during the purge mode and therefore,the purge air has a greater capacity to pull water out of the desiccantduring the purge cycle that follows.

Accordingly, a method for drying air in the air-brake system of acommercial vehicle includes passing compressed air against a surface ofa wall that is in contact with purge air before passing the compressedair through the desiccant. When the compressed air and purge air contactopposite sides of a common wall a heat exchange occurs and the decreasein temperature of the compressed air is gained is reflected in theincrease in the temperature of the purge air. The temperature gradientsof the compressed air and the purge air can vary during the cycledepending upon many factors, including but not limited to, the physicalarrangement of the components in the air brake system, the length of thecompressed-air conduit, the material composition of the conduit, etc.Compressed air entering the inlet port 19 of purge-air reservoir housing24 can range for example, from about 150° C. to about 250° C. and maydrop several degrees after traveling through heat-exchange dryerapparatus 10.

The desiccant material 40, which can be for example a beaded desiccantmaterial, adsorbs moisture and other contaminants, such as oil, from thepressurized air. The desiccant material is placed inside the cartridgevia an enclosure that typically has a generally circumferential wall andcreates an annular space between the desiccant material and thedesiccant cartridge. A spring 64 maintains pressure on the desiccantmaterial 40 to inhibit movement in the desiccant, for example thedesiccant beads.

The vessel or housing 24 of the purge-air reservoir 23 is shown as atwo-piece casting 60 and 62, however, in another embodiment the vesselor housing can be an integral or single unit. The top and bottomcastings 60, 62 are held together with crimp band 64 via crimp fitting65 and nut 79. However, the two portions of the reservoir can be securedby a bolt or some other conventional fastening or attachment means. Thevessel or housing 24 of the purge-air reservoir 23 also includesmounting brackets 66 and 67 (shown in phantom) to secure onto thevehicle.

FIG. 3 is a perspective view of another heat-exchange dryer apparatus 80showing internal components, according to an embodiment of the presentinvention. Many of the same components such as the governor 14, thepurge valve assembly 71, and supply port 52 are included as inheat-exchange dryer apparatus 20 of FIG. 2 but are viewed from anotherdirection. Heat-exchange dryer apparatus 80 has a compressed-air conduit82 that extends between an inlet port 19 (FIG. 1) at a proximal end 84and the desiccant cartridge 22 where it is secured by optional coupling98. Alternatively, compressed-air conduit and treated-air conduit 50 canalso be secured by integral couplings 49 and 53 of the housing 24 of thepurge-air reservoir as shown in FIG. 2. Treated-air conduit 92 isdisposed between coupling 98 and the supply port 52. Compressed-airconduit 82 that has a greater length than the compressed-air conduit 44(FIG. 2) and therefore has a greater surface area for heat transfer. Thewinding bends allow for greater length and surface area in the allocatedspace of purge-air reservoir and housing 24.

In another embodiment of the invention FIG. 4 shows a schematicrepresentation of commercial vehicle air brake system 100 in accordancewith another embodiment of the present invention. In this embodimentheat-exchange dryer apparatus 102 includes compressed-air conduit 104(shown in cross-section), a vessel or shell 108 of a purge-air reservoir107, and desiccant cartridge 120 containing desiccant 121. In thisembodiment the compressed-air conduit 104 and the purge-air reservoirshell 108 are remote from the desiccant cartridge 120 and desiccantmaterial 121. In addition, purge-air reservoir shell 108 is nestedwithin the compressed-air conduit 104.

The charge and purge modes of commercial vehicle air-brake system 100 issimilar to that as described according to that described above withrespect to system 10 (FIG. 1). During the charge cycle the compressedair flows through outlet port 13 of compressor 12, through compressordischarge line 18, and through inlet port 105 of compressed-air conduit104. The compressed air then flows around vessel wall or shell 108of-purge-air reservoir 107 and exits through port 106 and through line112 to inlet port 114 of desiccant cartridge 120. The air passes throughthe desiccant 121 and the treated air exits the dryer cartridge throughsupply line 26 to supply tank 30. A portion of the treated air is sentback to the purge reservoir 107 through port 109 of shell 108 viatreated-air conduit 122. The purge air remains inside purge-airreservoir shell 108 throughout the charge cycle. The temperature of thepurge air increases as the temperature of the air in the compressed-airconduit 104 decreases. Once the supply tanks and system have reached thecutout pressure, the compressor stops and the purge mode begins. Thepurge air flows out of port 109 and enters the dryer cartridge 122 toregenerate the desiccant 121.

In any of the embodiments described above, heat-exchange dryer apparatuscan further include a baffle or fin to direct air flow and facilitateimproved heat transfer between the compressed air and the cooler purgeair. FIG. 5 is an expanded view cross-sectional illustration of thecompressed-air conduit 104 and purge-air reservoir shell 108 portions ofheat-exchange dryer apparatus 102. The cut-away portion of purge-airreservoir shows shell or wall 108 which is contacted on one surface, theoutside surface, by compressed air flowing through the compressed-airconduit 104 and contacted on the opposite surface, the inside surface,by air flowing in and out of the purge-air reservoir shell 108. In thisembodiment, the shell 108 of the purge-air reservoir 107 and thecompressed-air conduit have a common wall. The purge-air of thepurge-air reservoir and the compressed-air of the compressed-air conduitcontact opposite surfaces of the same wall. The heat transfer can beincreased by fin 130, for example a spiral fin, which directs airflowing into port 105 of the compressed-air conduit and spiraled acrossshell 108 until the air reaches outlet port 106 and out of the purge-airreservoir shell. Fin 130 provides greater surface area through whichheat is conducted and facilitates greater temperature changes in thecompressed air flowing through the compressed-air conduit 104 and thepurge air inside shell 107 inside purge-air reservoir 108. It should beunderstood that several other alternative designs to facilitate heattransfer can be employed. The wall 108 of purge-air reservoir 107 ismade of a material that has a high heat transfer coefficient, forexample, a heat transfer coefficient that is at least about 100 W/mK.The purge-air reservoir shell 108 can be made of high thermalconductivity materials, including but not limited to, aluminum, copper,gold, silver, brass and alloys or mixtures thereof.

FIG. 6 is a schematic illustration of a portion of heat-exchange dryerapparatus 132 that can be used in commercial vehicle air brake system100 of FIG. 4, according to an alternative embodiment of the presentinvention. In this embodiment vessel or shell 140 of purge-air reservoir142 is remote from the desiccant dryer 120 similar to the embodiment ofheat-exchange dryer apparatus 102 of system 100 described with respectto FIG. 4. The compressed-air conduit 144 containing hot compressed gas146 is nested in the vessel or shell 140 of the purge-air reservoir 142.Compressed air flowing from the compressor 12 through compressordischarge line 18 enters inlet port 150 of the compressed-air conduit144 that is at least partially surrounded by the shell 140 of purge-airreservoir 142, and exits port 152 via conduit 112 to dryer desiccantinlet 114 (FIG. 4). A portion of the treated air exiting desiccant dryer120 is routed to the vessel or shell 140 of the purge-air reservoir 142via conduit 122 and into the vessel or shell of purge-air reservoir 142via port 154. The purge air can also exit through conduit 122 or anotheroptional port of the purge-air reservoir vessel or shell 140 toregenerate the desiccant material. The wall or compressed-air conduit144 is contacted on one surface, the inside surface, by compressed airand contacted on the opposite surface, the outside surface, by airflowing in and out of the purge-air reservoir 142. That is, a wall ofpurge-air reservoir 142 and the compressed-air 146 have a common wall inthe compressed-air conduit 144, and the purge-air of the purge-airreservoir and the compressed-air of the compressed-air conduit contactopposite surfaces of the same wall 144. Heat-exchange dryer apparatus132 can optionally include a fin 130 (FIG. 5), for example a spiral finwhich directs air flowing into port 154 purge-air reservoir 142. Fin 130provides greater surface area through which heat is conducted andfacilitates greater temperature, i.e. to decrease the temperature of thecompressed air 146 flowing through the compressed-air conduit 144 and toincrease the temperature of the purge air inside vessel or shell 140 ofpurge-air reservoir 142. It should be understood that several otheralternative designs to facilitate heat transfer can be employed.

While the present invention has been illustrated by the description ofembodiments thereof, and while the embodiments have been described inconsiderable detail, it is not the intention of the applicants torestrict or in any way limit the scope of the appended claims to suchdetail. Additional advantages and modifications will readily appear tothose skilled in the art. It will be appreciated that components of theheat-exchange dryer apparatus, for example such as the desiccant, thepurge reservoir and the compressed-air conduit, may adopt a wide varietyof configurations and be secured to the vehicle air system in a varietyof manners. Therefore, the invention, in its broader aspects, is notlimited to the specific details, the representative apparatus, andillustrative examples shown and described. Accordingly, departures maybe made from such details without departing from the spirit or scope ofthe applicant's general inventive concept.

What is claimed is:
 1. A heat-exchange dryer apparatus for a vehicleair-brake system, the apparatus comprising: a desiccant cartridgecomprising desiccant material; a housing of a purge-air reservoirsecured to the desiccant cartridge; a compressed-air conduit disposedinside the housing of the purge-air reservoir and in fluid communicationwith the desiccant material.
 2. The heat-exchange dryer apparatus ofclaim 1, wherein the compressed-air conduit is disposed inside thehousing of the purge-air reservoir such that the compressed-air conduitis surrounded by purge air contained in the purge-air reservoir.
 3. Theheat-exchange dryer apparatus of claim 1, wherein the compressed-airconduit comprises a material having a heat transfer coefficient that isat least about 100 W/mK.
 4. The heat-exchange dryer apparatus of claim1, wherein the compressed-air conduit comprises a material selected fromthe group of: aluminum, copper, brass, gold, silver and alloys thereof.5. The heat-exchange dryer apparatus of claim 1, wherein thecompressed-air conduit is in fluid communication with an inlet port ofthe housing of the purge-air reservoir and the desiccant material. 6.The heat-exchange dryer apparatus of claim 1, wherein the compressed-airconduit has a first end secured to an inlet port of the housing of thepurge-air reservoir and a second end secured to an outlet port of thehousing of the purge-air reservoir.
 7. The heat-exchange dryer apparatusof claim 1, wherein the compressed-air conduit has a first end securedto a purge-valve assembly of the housing of the purge-air reservoir anda second end secured to the housing of the purge-air reservoir.
 8. Theheat-exchange dryer apparatus of claim 1, further comprising atreated-air conduit disposed inside the housing of the purge-airreservoir.
 9. The heat-exchange dryer apparatus of claim 8, wherein thetreated-air conduit comprises an opening that allows the treated air toflow between the treated-air conduit and the purge-air reservoir insidethe housing.
 10. The heat exchange dryer apparatus of claim 1, whereinthe desiccant material is contained in a desiccant enclosure and thedesiccant enclosure is positioned inside the desiccant cartridge to forman annular space between the desiccant cartridge and the desiccantenclosure; and the compressed-air conduit is in fluid communication withthe annular space inside the desiccant cartridge.
 11. The heat-exchangedryer apparatus of claim 1, wherein the compressed-air conduit insidethe housing of the purge-air reservoir comprises a shoulder and a sealdisposed thereon.
 12. The heat-exchange dryer apparatus of claim 1,wherein the compressed-air conduit inside the purge-air reservoir isoriented at an angle relative to a horizontal x-axis.
 13. Theheat-exchange dryer apparatus of claim 1, wherein the compressed-airconduit inside the housing of the purge-air reservoir does not have botha positive and negative slope.
 14. The heat-exchange dryer apparatus ofclaim 8, wherein the treated-air conduit is in fluid communication withthe desiccant material and has a first end that is secured to an inletport of the housing of the purge-air reservoir and a second end securedto an outlet port of the housing of the purge-air reservoir.
 15. Theheat-exchange dryer apparatus of claim 1, wherein the compressed-airconduit comprises aluminum.
 16. A heat-exchange air dryer apparatuscomprising: a desiccant cartridge comprising desiccant material; acompressed-air conduit in fluid communication with the desiccantmaterial; and a shell of a purge-air reservoir disposed remote from thedesiccant cartridge and nested in the compressed-air conduit.
 17. Theheat-exchange dryer apparatus of claim 16, wherein the shell of thepurge-air reservoir and the compressed-air conduit share a common wall.18. The heat-exchange dryer apparatus of claim 16, wherein the purge-airreservoir comprises a material having a heat transfer coefficient thatis at least about 100 W/mK.
 19. The heat-exchange dryer apparatus ofclaim 16, wherein the purge-air reservoir comprises a material selectedfrom the group of: aluminum, copper, brass, gold, silver, and alloysthereof.
 20. The heat-exchange dryer apparatus of claim 16, wherein thecompressed-air conduit comprises aluminum.
 21. The heat-exchange dryerapparatus of claim 16, further comprising a baffle to redirect the flowof compressed air in the compressed-air conduit.
 22. The heat-exchangedryer apparatus of claim 16, further comprising a fin that extends fromthe shell of the purge-air reservoir and inside the compressed-airconduit.
 23. The heat-exchange apparatus of claim 16, further comprisinga purge-air conduit in fluid communication with the desiccant materialand the purge-air reservoir.
 24. A vehicle air-brake system comprising:an air compressor; a heat-exchange dryer apparatus comprising: adesiccant cartridge comprising desiccant material; and a first vesseland a second vessel disposed between the compressor and the desiccantmaterial, wherein the second vessel is nested in the first vessel. 25.The vehicle air-brake system of claim 24, wherein the second vesselcomprises a material having a coefficient of thermal conductivity thatis at least about 100 W/mK.
 26. The vehicle air-brake system of claim24, wherein the second vessel comprises a material selected from thegroup of: aluminum, copper, brass, silver, gold, and alloys thereof. 27.The vehicle air-brake system of claim 24, wherein the second vessel ismade of a material comprising aluminum.
 28. The vehicle air-brake systemof claim 24, wherein the first vessel is a housing of a purge-airreservoir and the second vessel is a compressed-air conduit.
 29. Thevehicle air-brake system of claim 24 wherein the first vessel is acompressed-air conduit and the second vessel is a shell of a purge-airreservoir.
 30. The vehicle air-brake system of claim 28, wherein thehousing of the purge-air reservoir is attached to the desiccantcartridge.
 31. The vehicle air-brake system of claim 28, wherein thefirst vessel and the second vessel are remote from the desiccantcartridge.
 32. The vehicle air-brake system of claim 29, wherein theshell of the purge-air reservoir is remote from the desiccant cartridge.33. The vehicle air-brake system of claim 28, wherein the purge-airinside the housing of the purge-air reservoir and the compressed-air ofthe compressed-air conduit contact a common wall.
 34. The vehicleair-brake system of claim 33, wherein the common wall comprises amaterial selected from the group of: aluminum, copper, brass, silver,gold, and alloys thereof.
 35. A method for drying air in an air-brakesystem of a commercial vehicle comprising: passing compressed airflowing within a compressed-air conduit against a first surface of awall that is in contact with purge air residing in a purge-air reservoiron an second surface of the wall opposite the first surface; and passingthe compressed air through a desiccant material after contacting thewall to produce treated air.
 36. The method of claim 35, wherein passingthe compressed air against the wall increases the temperature of thepurge air and decreases the temperature of the compressed air.
 37. Themethod of claim 35, wherein the wall has a heat transfer coefficient ofat least about 100 W/km.
 38. The method of claim 35, wherein the wallcomprises a material selected from the group of: aluminum, copper,brass, gold, silver and alloys thereof.
 39. The method of claim 35,wherein compressed-air conduit is disposed within the purge-airreservoir.
 40. The method of claim 35, wherein the purge-air reservoiris secured to a desiccant cartridge comprising desiccant material. 41.The method of claim 35, wherein the purge-air reservoir is nested insidethe compressed-air conduit.
 42. The method of claim 35, furthercomprising: passing a portion of the treated air into the purge-airreservoir; and passing the treated air in a reverse direction throughthe desiccant.